Pressure-expansion rotary engine



Jan. 21, 1947. I c. M. TUMEY ET AL 2,414,779.

I PRESSURE-EXPANSION ROTARY ENGINE Filed May 26. 1944 6 Sheets-Sheet 1 INVEHTORJ,

Char/e5 771112 am] far] E.Bow'er5 M 4. mm

A2l'orne c. M. TUMEY ET AL PRESSURE-EXPANSION ROTARY ENGINE 6 Sheets-Sheet 2 Filed May 26, 1944 8 n: Y r n5 T m? an mu Mm RT 1 l A Horng c, M. TUMEY HAL PRESSURE-EXPANSION ROTARY ENGINE a Sheets-Sheet 4 Filed May 26, 1944 u a a y im twm Rmr n o ue r W B W C. M. TUMEY ETAL PRESSURE-EXPANSION ROTARY ENGINE m a J Filed May. 26, 1944 e Sheets-Sheet 5 INVENTOR ha /ea #720 112 qnJ Ear-l E, Bowers,

Attorney Jan; 21, 1947. c. M. TUMEY ETAL 2,414,779

I PRESSURE-EXPANSION ROTARY ENGINE Filed May 26, 1944 6 Sheets-Sheet 6 o 51 l 4 l1 mvsnrows,

Patented Jan. 21, 1947 UNITED STATES PATENT OFFICE 2,414,779 PRESSURE-EXPANSION ROTARY ENGINE Charles M. Tumey, Indianapolis, and Earl E. Bowers, Lebanon, Ind., assignors to Universal Corporation, a corporation of Indiana Application May 26, 1944, Serial No. 537,442

11 Claims.

This invention relates to a, rotary, pressure type engine wherein a fluid is admitted into the juncture of two annular chambers to drive intermeshing geared rotors in opposite directions within those chambers. A primary object of the invention isto provide a reversible engine of that type constructed in a very compact manner to achieve the highest possible thermal, as well as mechanical eificiencies.

Another important object of the invention is to provide multiple expansion of the operating fluid with direct inner flow of fluids between various stages. A still further important object of the invention is to provide a valve means for controlling the flow of the fluid between the various stages of the engine to confine such flows to the minimum length of travel.

These and other importantobjects and advantages of the invention will become apparent to those versed in the art in the following description of one particular form of the invention as illustrated in the accompanying drawings, in which Fig. l is a view in rear end elevation;

Fig. 2, a view in central vertical longitudinal section on the line 2-2 in Fig. 1;

Fig. 3, a view in central transverse longitudinal section on the line 3-3 in Fig. 2;

Fig. 4, a transverse vertical section on the line 6-4 in Fig. 2;

Fig. 5, a view in transverse vertical section on the line 5-5 in Fig. 2;

Fig. 6, a detail on an enlarged scale in perspective of ayalve structure; and

Fig. 7, a view in transverse vertical section on the line 1-1 in Fig. 2.

Like characters of reference indicate like parts throughout the several views in the drawings. Upper and lower stepped rotor shafts l and II respectively are supported in spaced apart relation to have the axes in a common vertical plane by bearings, preferably roller bearings l2 on outer end portions of the shafts mounted respectively in the front and rear bearing heads l3 and I4.

Fixed on the upper shaft I0 are a plurality of gear like rotors consisting of the center high pressure rotor l5, an intermediate pressure rotor I6 to the left, Fig. 2; a low pressure rotor I! to the left of the rotor I6; an intermediate pressure rotor [8 to the right of rotor I5, and a low pressure rotor P9 to the right of the rotor [8. In like manner the lower shaft II carries the corresponding and intermeshing rotors 20 to mesh with rotor l; 2! to mesh with rotor I6; 22 to mesh with inder side plate 2 rotor ll; 23 to'mesh with rotor mesh with rotor IS.

The high pressure rotors I5, 20, have the narrowest longitudinal length of face; the faces of the intermediate and low pressure rotors increasing respectively in width. While each of the named rotors may he formed in one piece, for convenience in manufacturing, each rotor is made of two sections coming together face to face in a plane centrally of the longitudinal length of the combined pieces.

A central high pressure cylinder plate 25 is provided with longitudinal bores 26 and 21, Figs. 2 and 4, the two chambers opening one into each other through a chordal plane, through which opening the gears I5 and 20 inter-mesh.

To the left of the cylinder plate 25 is a cyl- 28 abutted against the cylinder plate 25 and fitted within an aligning cylinder 29. This side plate 28 extends along and around the left hand faces of the rotors l5 and 2E] and preferably forms seals therebetween in any suitable manner, such as by a series of labyrinth rings 30 for each rotor. Against the left hand side of the side plate 28 is an intermediate cylinder plate 3i having upper and lower cylinders intercommunicating to surround the rotors l6 and 2| and permit their meshing through the opening between those cylinders in the same manner as indicated for the high pressure unit. This intermediate cylinder plate 3| is axially located within the cylinder 29 to abut the side plate 28, whereby that plate formsthe right hand side walls of the upper and lower cylinders carrying the rotors Iii and 2|, and also serves to form the seal against the right hand sides of those two rotors.

A side plate 32 is slidingly fitted within the cylinder 29, the same as the side plate 28, and is abutted against the left hand face of the cylinder plate 3! to form seals around the rotors It and 2t. All of the rotors have hubs which extend along the respective shafts Ill and H and which freely pass through openings in the plates 28 and 32.

. Abutting the left hand side of the side plate 32 is the low pressure cylinder plate 33 which is provided with cylinders opening one into the other and within which the rotors I! and 22 are contained. This cylinder plate 33 fits within the cylinder 29 with a sliding fit. A similar side plate 34 is slidingly fitted within the cylinder 29 to abut the left hand side of the cylinder plate 33 and to form seals around the left hand faces of the upper and lower rotors I1 and 22 respecl8; and 24 to tively. The front bearing head i3 has a right hand face to bear against the side plate 34 and also the end of the cylinder 29. The aligning cylinder 29, by its right hand end, abuts the high pressure cylinder plate 25.

On the right hand side of the high pressure cylinder plate is an aligning cylinder within which is slidingly fitted in consecutive order the side plate 35 between upper rotors l5 and I8 and the lower rotors 2t and 23; the intermediate pressure rotor plate 31 within which rotors i8 and 23 are carried; the side plate 38 enclosing those rotor cylinders on the right hand side and form-' ing seals with the same rotors, and also forming seals with the low pressure rotors l3 and 2 the low pressure cylinder plate 39 abutting the side plate 33 and having cylinders within which the rotors l3 and 2t revolve; and the end plate 453 abutting the cylinder plate 39 and forming seals with the rotors l8 and 24. The rear end bearing head It abuts the end plate iii and also the outer end of the aligning cylinder 35. A plurality of through bolts M pass through ears of the bearing heads l3 and id to compressibly engage therebetween all of the various plate elements recited. Surrounding the aligning cylinders 29 and 35 is a jacket 42 to carry between it and those cylinders insulating material it to prevent. loss of heat.

Referring to Fig. 4 wherein rotors l5 and 26 are shown in side elevation, that is transversely of the axes of the shafts it? and I l, the rotor it: has its major peripheral portion out to form gear teeth M, the outer ends of which are spaced inwardly from the circumferential wall of the cylinder in which it appears in the plate 25 so as to leave an opening around the rotor therebetween. This opening however is interrupted by a major toot-h the outerend of which is in substantially sliding contact with the circumferential wall of the cylinder 2%, and then- 90 degrees around from that to'oth Z5- is the second major tooth 46 likewise extending radially outwardly into substantially sliding contact with the wall of the cylinder 26, to be followed by a third major tooth 41 extending tothewallor the cylinder to revolve therearound.

. Between teeth Alfiand the minor teeth M continue. The lower rotor 23 is likewise provided with teeth 58 around the major circumferential length "thereof tohave their outer ends spaced inwardly from the circumferential wall of the cylinder 21 to leave an annular passageway therearound. The rotor at is provided with a major tooth 59 and the minor teeth of the two rotors l5 and 2t are'so meshed throughthe opening between the cylinders 26 and 2'? that the tooth 49 will mesh between the teeth 46 and ll inv driving relation therewith, as well as in sealin}; relation. The rotor 2G is further provided with the major teeth 5i? and iii between which the tooth 15 of the rotor l5 will mesh in sealing and driving relation so that rotation of one rotor about its axis will cause continuous rotation of the other rotor about its own axis without any interruption in the drive.

All of the other pairs of rotors have the same diameters and are formed to have peripheral teeth both minor and major, in exactly the same manner as has been described in relation to rotors I5 and 20, the only difference in the rotors being that from the high pressure pair of rotors, the rotors increase in width for the intermediate pressure rotors and the low pressure rotors, all .as indicated in Fig. 2.

- Still referring to Fig. 4,- ailuid admission valve of two parts. two side plates 1 5 and 16 together through a 4 52 is mounted to center over the high pressure cylinder 25. While it is conceivable that a range of fluids may be employed, the present invention will be described a using steam, preferably high pressure, high temperature, super-heated steam. .A valve plug 53 is mounted within the valve 52 to be turned on a horizontal axis by means or an externally presented throttle lever 54, Fig. l. The plug 53 is provided with a chordal passageway 55 thereacross so that the plug 53 may be turned to have this passageway 55 selectively register with the intake passageway 56 and a discharge passageway 5'! both carried within the valve 52, or for reversing purposes the plug 53 may be turned to have the plug passageway 5E3 intercommunicate between the intake passageway 56 and with the discharge passageway 58.

In the position of the plug 53 as shown in Fig. 4, steam is admitted through the intake passageway 56 then through the plug passage 55 to travel through the valve discharge passage 5'! and enter a steam conduit 59 provided within the cylinder plate 25 to extend around outside of the cylinder 25 and by diverging ways 6d and 6! open into the cylinders it; and 21 respectively to direct steam essentially in the directions of rotations of those rotor i5 and 259 therein. The openings from the ways 53 and 6! are spaced circumferentially from the chordal plane across the intersection of the two cylinders.

In like manner, for reverse driving of the rotors i5 and 23 and consequently of the shafts l9 and H the valve plug 53 upon having its passage 55 turn to communicate between passages 56 and 53, will permit steam to flow through the conduit 62 provided around on the opposite side of the cylinder 5%, from which conduit 62 steam may pass through the diverging ways 63 and 65 into the respective cylinders 26 and 2'! circumferentially around in the direction of travel of the rotors from the opening between the two cylinders.

The shaft it is drivingly connected with the shaft ll; through spur gears, 8'35 and 65, the drive being taken through these gears from the shaft IE! to the shaft H; While all of the rotors are intermeshed in pairs through their respective teeth, the rotor teeth serve primarily as sealing means and not driving means, the inter-meshing of the minor teeth on the rotor serving to prevent inner-flow of steam across from one side of the inter-meshing to the other side.

From the shaft H extends a drive, Fig. 3, herein shown as a train of two gears 88 to drive a rocker shaft 81: which extends revolvably through the plate 36 to rock on a lower pivot pin H and extend upwardly therefrom. Through an openi'ng in the rocker lilextends the shaft 6! to have a cam '52 thereon against which on opposite sides bear the shoes 13 so that turning of the shaft 61 will cause the rocker Hi to oscillate about its pivot H. The rocker '69 is mounted and operated in the same manner in' the side plate 28. As indicated in Figs. 2, 3, and 5 primarily, the side plate 36 is provided with a slot "M cut trans- Versely and across its entire face. Within that slot is mounted a slide valve consisting essentially One part is built up by securing dinal opening of the window 89.

between within which the other element consisting of a slide bar 18 may reciprocate. 'This I slide bar 18 is connected through a link 79 with the upper end of the rocker whereby turning of the shaft 9'! will cause the rocker "I9 to reciprocate the slide bar I8 within the slot 19 and between the two side plates 75 and IS, the top and bottom faces of the slot "i l being contacted slidingly by the respective top and bottom edges of the bar 18. The slide bar I8 has a window 89 therethrough adjacent the inner end. The plate I6 is provided with a pair of windows 9| and 82 spaced apart a distance exceeding the longitu- The other plate 75 is also provided with a pair of windows 83 and 84 spaced closer together than are the windows in the plate 76, the vertical edges of these windows being so arranged that the opposing edges of the window 8i are in common opposite planes of the edges of the window 83, these two opposing planes being diagonally disposed, whereas the vertical opposing edges of the window 82 are in common opposing planes with the like edges of the window 89.

Through the right hand portion of the plate 39 back of the valve slot 79 is positioned a window 85 opening from the juncture of the cylinders in the cylinder plate 97 back of the inter-meshing .teeth of the upper and lower rotors I9 and 23 and extending horizontally and diagonally to the left to have its vertical edge faces in alignment with i a corresponding window 89 entering a valve cover plate 8? from the forward side of the inter-meshing teeth of the rotors I5 and 29 and the high pressure cylinders, it being understood that the valve elements I9, 76, and I9 are disposed therebetween. This valve plate 81 carries a second window 99 on the other side of the inter-meshed teeth of those rotors I5 and 29 to extend diagonally in line with the vertical edges of an opening 89 in the side plate 39 to the right of the valve elements to open into the cylinder space on the other side of the inter-meshed teeth of the rotors I8 and 23 in respect to the window 85. In the position shown in Fig. 3, the windows 98, 9t, 83, and 89 are all in alignment diagonally across the side plate 96, and the valve slide bar I8 is positioned to have its window 89 within this diagonal passage-way whereby steam may escape from the high pressure cylinder across the side plate39 into the intermediate pressure cylinder.

Reciprocation of the slide bar I8 carries the window 89 out of register with that diagonal passage-way whereby that passage-way is intermit-- tently opened and closed thereby all through the turning of the shaft 9? to rock the arm Ill.

The right hand end of the valve element, Figs. 5 and 6, comprising the bars l5 and I9 has teeth out in the under edges of those bars to form a rack gear to mesh with a pinion ear 99 that is fixed to a valve shifter shaft 9I which extends forwardly through the various plates to terminate by an end exposed at the rear of the engine, Figs. 1 and 3, to be operated by a hand lever 92. Rocking the shaft 9i will change the position of the plates 15 and 76 along the slot 19 and accord- V ingly vary the positions of the windows 9i and 89 in respect to the slide bar window 89.

To reverse the direction of flow of the fluid as between cylinders in the plates 25 and 31, the hand lever 92 is rocked from the position shown in Fig. 1 to shift the valve elements 15 and 19 away from the stop pin I98, Fig. 5, toward the left of the slot M to bring the window 84 into register with the window -85, Fig, 3, and the Window82 into register with the window 89 thereby closing off flow through windows 89 and 89 and permitting a flow from window 89 through window 82, window 8, of the reciprocating bar I8, window 84 and window 85, it being understood that this passage-way would be intermittently opened and closed by a reciprocation of the bar 19 to bring the window 89 into and out of registry of that passage-way. In other words, when the engine is to be reversed in direction, not only is the fluid inlet valve plug 93 shifted, but this shaft 9| must also be shifted to change the valve elements I5 and I6 as described.

The high pressure cylinder plate 25 is also provided with outlet openings 93 to the back of the inter-meshing rotor and 94 to the front thereof, these openings being windows in the side plate 29 opening into a transverse slot 95 cut across the left hand face of the plate 28. In this slot is slidingly fitted spaced apart valve plates 99 and 9? anchored at their front hand ends one in respect to the other and reciprocated within the slot by means of the spur gear 98 which is fixed to the shaft 91 whereby the members 96 and 9'! are simultaneously shifted along with the shifting of the valve plates I5 and I6 in the slot '14. The valve plate 9! is provided with spaced apart windows therethrough 99 and I99 respectively. The other plate 99 has the windows WI and I92 spaced apart to be diagonally in line respectively with the windows 99 and I99, the windows I 9| and I2 being nearer together than are the windows 99 and I99. A reciprocatin bar I03 is linked to the rocker 99 and carries a window I04 out of registry in the positions of the elements shown in Fig. 3 with a passage-Way defined by the windows 93, 99, I 9|, and I95, provided in the valve slot cover plate I99 to the right of the inter-meshing rotor in the cylinder plate 3|. When the valve members 99 and 97 are shifted to the left to have the window I99 register with the window 94 and the window I92 register with the window I9! in the valve plate I99, the reciprocating bar window I99 will then intermittently register with the passage-way then defined through the window 94, window I99, window I92 and window I91.

In the side plate 32 is cut a central horizontal slot I98 within which is slidingly mounted a single valve bar I99 having a diagonal passage-way I I9 therethrough registering in the position indicated in Fig. 3 with a window I II to the back of the intermeshing rotors in the cylinder plate 3| and also with a window H2 formed in the slot cover plate I 3 to the front of the inter-meshing rotors in the cylinder plate 33. This valve bar I09 is further provided with a diagonal passageway I I4 therethrough which, upon the bar being shifted to the back will register with the window H5 in the side plate 32 opening to the front of the inter-meshed rotors in the cylinder plate 3| and the window I I6 in the slot cover .plate I H to the back of the inter-meshed rotors in the cylinder plate 39. The shifting of this valve bar I99 is accomplished by means of a spur gear I I1 fixed to bar H8 is provided with a passageway [2| theret-h'rough registering in the position shown in Fig. 3 with a Window I22 in the side plate 33 opening on the back side of the intermeshed rotors in the cyimd plate 353 and also with an exhaust port Iii-3. When the bar H8 is in its back position, a second passageway lfi thereacross will register with the window 525- in the side plate 3 3 opening tqthe front of the inter-meshed rotors in the cylinder plate 33 and also with the exhaust port 123.

The side plate 38 has a slot i226 cut horizontally and centrally across its le'fth'and face to receive therein the valve slide bar [21 to be re'ciprocated within the slot by means of the s'pur gear I28 fixed on the shaft 9|. This slide bar i2! is provided with a diagonal passage-way I29 thereacross registering in the position indicated in Fig. 3 with the window B36 in the slot cover plate l3! opposite the window 85 across the cylinder plate 31 and with the Window i3! through the side .plate 38 to the front of the inter-meshed rotors the cylinder plate 39. The bar l2! also carries a second diagonal passage-way I33 which, when the bar I21 is shifted to the back in its slot, will register with the window I34 of the cover plate 13] and the window I35 in the side plat 38 to reverse the direction of flow. The side plate 48 has a slot i556 out across its right face centrally and horizontally thereacross within which is slidingly mounted the slide bar 13'! shifted by means of the spur gear i321 fixed to the shaft 9!. This bar [3? carries the oppositely directed cross passage-Ways I39 and Me selectively registering with the window Hi! in the left face of the side plate 48 and the exhaust port M3 in the position shown in Fig. 3, and when the bar it? is shifted, the passage-way Mt) will register with the window M2 and the exhaustport 1 4 3. 7 V

The gears of the train at operate the rocker shaft 6? at twice the speed of the shaft i i and the rockers 6S and iii are mounted in relation to the operating cams on the shaft 61 to reciprocate in opposite directions whereby, for example, the slide bar it; will be in the open position when the slide bar its is in the closed position during one half of the shaft l l revolution and vice versa during, the other half;

With this timing of the travel ofthe slide bars :8 and 103, during the first half of the shaft H revolution as indicated in Fig. 3, and with the valve plug 53 in the position shown in Fig. 4, steam will be admitted through the passageway 59 to drive the high pressure rotors I5 and 28 in the directions of the arrows as shown in Fig. 4, steam flowing through the way 69 into the chamber 26 to follow around against the tooth d? in a counter-clockwise direction, and also howing through the Way 6! to follow in clockwise direction around the cylinder 27 against the tooth 49, and thereafter, as the teeth 45 and 5!, 5!! pass the ways 63 and 5! respectively, against the teeth 45 and 59. After the teeth 46 and 4'! pass the passageway to steam between the teeth 45 and 41 and between the teeth 5! and 59 will escape from the back side, Fig. 3, of the intermeshing teeth M and 48 through the passageway defined by the openings 88, Bl, 89, as, and 89 into the plate 31 forwardly of the inter-meshing teeth so as to apply pressure todrive the rotors i8 and 23 in the same directions respectively as the turning of the high pressure rotors l5 and 2%. Continuing with the rotation of the rotors, steam will escape from the backside of the inter-mesa ing rotors I8 and 23 through the passageway defilled by the openin s I35, I29, and I32 forward- 1y 0f the inter-meshing rotors 1-9 and 24 to have that steam expand arid aid in turning those rotors in the same relative directions as the upper and lower rotors in the other chambers. From the back side of the rotors l9 and 24, steam finally es'capes through the passageway MI, I39 and 143 of the exhaust conduit. It is to be understood, of course, that the bars I21 and 13-! remain stationary at all times and are only shifted when the engine is to be reversed in direction of rotation. V v

, Now, with the slide bar 33 in the closed position as indicated in Fig. 3 rotors l6, 2] and H, 22 are being driven only under expansive pressure of the steam previously admitted during another cycle and with the two to one drive ratio between the shafts l I and 81, these slide bars 78 and H13 reciprocate to alternately open and close passageways first for direct flow from the high pressure rotors l5 and 20 to the right hand rotors, Fig. 3, during the first half cycle of myolution of shaft II and during the second half to have steam flow from those high pressure rotors to left hand rotors.

In other words during the first half 'revolution, steam will be admitted to the right hand rotors, Fig. 3, and during the second half of that revolution steam will beadrnitted from the high pressure rotors to the left hand rotors. In other words steam is intermittently supplied to the right and left hand sides of the high pressure rotors to flow and expand first between the intermediate sets of rotors and then the lower pressure rotors in the outer ends. ,7

To reverse the engine, all that is hecessary is to reverse the position of the plug 53, turning it in a counter-clockwise direction in reference to Fig. 4 to have the passageway 55 interconnect passageways 56 and 53; and also shift the reversin'g valve handle 92 around in a clockwise direction, Fig. 1. While labyrinth packing has been indicated above as desirable between the side faces of the rotors, and the adjacent side plates between cylinders, the leakage problem in the form of the invention herein shown is reduced to practically nothing since any steam escapingalong the sides of the rotors can only travel into the next rotor. The low pressure at the outer faces of the low pressure rotors induces very little tendency to leak in any event. In other words, the labyrinth packing may be omitted entirely to reduce resistance to turning of the various parts.

Therefore, while we have herein shown and described our invention in theon'e particular form in more o'r l'ess minute detail, it is obvious that structural changes may be embodied, particularly in the drive of the valves and the form of the intermeshing and drive teeth of the rotors, and in' the manner of forming the rotor cylinders of the rotors themselves, all Without departing from the spirit of the invention, and we, therefore, do not desire to be limited to thatprecise form any more than may be required by the following claims.

we claim:

1.'In a pressure type'rotar'y en'gihathe' combination of a plurality ofpairs of cylinders, in each pair of which one cylinder opens by a side chordally into the other cylinder; a bladed, gear rotor in each cylinder intermeshing acrosssaid chordal' opening with a like gear rotor in the other cylinder; said cylinders having passageways leading across from one side of the intermeshing or the rotors'm one pair of cylinders tothe other side of theintermeshing of rotors in-the adia- 'cent'cylinders; valve means intercepting said pasone cylinder pair.

2. In a pressure type rotary engine, the combination of a plurality of pairs of cylinders, in each pair of which one cylinder opens by a side chordally into the other cylinder; a bladed, gear rotor in each cylinder intermeshing across said chordal opening with a like gear rotor in the other cylinder; said cylinders having passageways leading across from one side of the intermeshing of the rotors in one pair of cylinders to the other side of the intermeshing of rotors in the adjacent cylinders; valve means intercepting said passageways leading from'each endof one of saidpairs of cylinders; and means driven by said rotors to operate said valve means to open and close alternately those passageways from said one cylinder pair; and reversing valve means carrying parts of said passageways to complete said passageways in one direction and close them 01f in the other direction by selective shifting of the reversing valve means; and means for shifting the reversing valve means. I I

3. In a pressure type rotary engine, two pairs of cylinders, one of each pair opening by a side into the otheracross a chordal plane; a rotor in each cylinder, each having minor teeth between the periphery of which and the cylinder Wallis defined an annular chamber, and a major tooth, the outer end of which is in substantial sliding contact with said cylinder wall, said rotors intermeshing across said openin spaced apart rotor carrying shafts, one for each set of rotors; a fluid inlet leading into'one pair of said cylinders adjacent to and on one side of the intermeshing portions of the rotors; said two pairs of cylinders having an exhaust passageway leading diagonally across from the discharge side of said intermeshing portions ofsaid one pair of cylinders to the second pair of said cylinders to the pressure side of their rotor intermeshed portions; and a valve shiftably intercepting said passageway operated from one of said shafts.

4. In a pressure type rotary engine, two pairs of cylinders, one of each pair opening by a side into the other across a chordal plane; a rotor in each cylinder, each having minor teeth between the periphery of which and the cylinder Wall is defined an annular chamber and a major tooth, the outer end of which is in substantial sliding contact with said cylinder wall, said rotors intermeshing across said opening; spaced apart rotor carrying shafts, one for each set of rotors; a fluid inlet leading into one pair ofsaid cylinders adjacent to and on one side of the intermeshing portions of the rotors; said two pairs of cylinders having a fluid passageway leading diagonally across from the discharge side of said intermeshing portions of said one pair of cylinders to the second pair of said cylinders to discharge therein on the pressure side of their rotor intermeshed portions; and a valve shiftably intercepting said passageway operated from one of said shafts; a plate between each pair of cylinders forming side walls thereof and having said passageways formed thereacross; and said valve means being mounted within said plate between said cylinders to travel in substantial parallelism with said plate.

5. In a pressure type multiple expansion, rotary engine, the combination of a plurality of pairs of cylindersarranged side by side with common partition walls therebetween, the cylinders in each pair opening one into the other from their sides on a common chordal plane; a rotor in each cylinder having peripheral teeth intermeshing across said opening to leave an annular chamber around each rotor, and a large gear shaped tooth extending to the inner cylinder wall; said partition walls having a valve chamber, adjacent the intermeshing of said rotors, having fluid openings therein from adjacent pairs of cylinders from both sides of their rotor intermeshing; and a valve member in said chamber for selectively opening and closing said openings; said valve member comprising a slidable bar; and means for reciprocating said bar across said openings in timed sequence with the travel of said teeth.

6. In a pressure type multiple expansiomrotary engine, the combinationof a pluralityof-pairs of cylinders arranged side by side with common partition walls therebetween, the cylinders in each pair opening one into the other from their sides on a common chordal plane; a, rotor in each cylinder having peripheral teeth intermeshing across said opening to leave an annular chamber around each rotor, and a large gear shaped tooth extending to the inner cylinder wall; with a valve chamber in said. partition walls, adjacent the intermeshing ,of said rotors, having fluid, o enings therein from adjacent pairs of cylinders from both sides of their rotor intermeshing; and a valve member in said chamber for-selectively opening and closing said openings; said'valve member comprising a slidable bar; and means for reciprocating said bar across said openings; a pressure fluid inlet leading into a central pair of said cylinders to one side ofand adjacent to the intermeshing of the rotors therein; and said bar reciprocating means being formed to recip rocate the valve bar on one side of said central pair of cylinders oppositely to the reciprocation on the other side. 7. In a pressure type multiple expansion, ro-

tary engine, the combination or a plurality of pairs of cylinders arranged side by side with common partition Walls therebetween, the cylinders in each pair opening one into the other from their sides on a common chordal plane; a rotor in each cylinder having peripheral teeth intermeshing across-said opening to leave an annular chamber around each rotor, and a large gear shaped tooth extending to the inner cylinder Wall; with a valve chamber in said partition walls, adjacent the intermeshing of said rotors, having fluid openings therein from adjacent pairs ofcylinders from both sides of their rotor intermeshing; and a valve member in said chamber for selectively opening and closing said openings; said valve member comprising a bar with passages thereacross for providing flows through said openings, selectively from opposite sides of said rotor intermeshings to adjacent cylinders.

8. In a pressure type multiple expansion, rotary engine, the combination of a plurality of pairs of cylinders arranged side by side with common partition walls therebetween, the cylinders in each pair opening one into the other from their sides on a common chordal plane; a rotor in each cylinder having peripheral teeth intermeshing across said opening to leave an annular chamber around each rotor, and a large gear shaped tooth extending to the inner cylinder wall; with a valve chamber in said partition walls, adjacent the intermeshing of said rotors, having fluid openings therein from adjacent pairs of cylinders from both sides of their rotor interanew beingheldstationary in one of two positions of 'fi W'throug'h said openings; and means for re,- eiprocatingsaid'secondvalve member to open ai i cse lte n y he passagewa e d by Said, v r i v b i.

9'; Ih' a; pressu e type, multiple expansion, r0 ta y ,'rig a plurality ofpairs' of ylinde'rs an r1 ge'dside by" Tsidlthe" cylinders in'each pair 6' ing bircurnferigntially"one into the other 20 a oss'a fchordalplane of intersection; a rotor n each" cyl nder hav ng e i he a nt imeshing across said intersection with the teeth for the'rotor of the intersectingeylinder, an annular chamber losing formedbetween said teeth and the Wall of eachchaniber, and a major tooth on each rotorektending tosaid Wall; crisscross passageways being provided between each pair of c linders cr s t e respective i e of id intermes ine' i an linde pa r t0 q e e sides in'the next adjacent pair; avalve chamber intereeptingsaid passageways; and a'valv'e member reciprocable in the chamber to provide flow t rou e c e Q said pa sa ew ys, and time ii e means c ua ing said va ve member in sequehce with th travel of said major teeth.

19, In a pressure type 'r'nultiple expansion, rotarjj enging'a plurality. of pairs of cylinders arranged side Icy side, the cylinders in each pair ripening circnrnferentially" pne' into the other across, a chordal plane of intersection; a rotor in each cylinder having peripheral teeth'intermeshing across said intersection with the teeth of h te le 9 h inier eet ng cylinder a an u ar b va ve me ber c ber be n c medeetween ale eeth and tf wa l o a h'ei embe and maie eeth 92 h re xtend n t ai wa l: i$$ 9$ Pasa' w pe e meet etween ea h a r at cylinders across" from respective sides of said intermshing in one cylinder pair toopposite sides n the next ad ace t hair; a valve c amb r 111-- t rt p sa as W s: an a valve member repi ee h e 1 he ehainbr 'te r iee lewrb h l t'eq 9f Said pa sa ew and seeit a eii t a ast a Part 9! ai fi st e' e' mf m e and re ie i e it! .11 seen te' e fire 'valve me ber tel easee an el i sa d sel cted assa ewa s "11 sl e t re m lt le eis ea re: tare theme the semina ei a My 91- nee 9 l iee e ar an e is eb steem an:

We pertiti e a i eae air o 5? .l erebetiveea cylind s Me qee e etee ,A en charge! Pl ne; ater 1e inde Wine eri hera tee h intenneshaid na e t ea e n eeaeler c anb er aph r92?! an a la e e r Sh r e et xteedi t9 h wee win er Wall; s c s men a a n a al e (membe emae i t' e i hi sale were Renee fluid Openings fih'r'eih mi ad eeeet winners t ee? both sides of their rotor 'interrneshing; and a valve member in said chamber jor selectively opening and closing said openings; said valve member comprisingaslidable bar; and means for reciprocating said bar across said openings in'tirned sequence with the travel of said teeth; said reciprocating means including means for reciprocating said bars in opposite directions on opposite sides of one of said airsloetween other pairs of cylinders whereby flow passageways sides on a co:

through said walls from said one pair of cyiinlo- AaLEs Tun reg. EA L r Q ER 

